Wheeled scraper



Dec 17, 1935.

J. H. SLAKER ET AL WHEELED SCRAPER Filed Sept. 12, 1932 9 Sheets-Sheet lWEN - 1935. J. H. SLAKER El AL 83 WHEELE'D SCRAPER Filed Sept. 12, 19329 Sheets-Sheet 2 rim WHEELED SCRAPER Filed Sept. 12, 1932 9 Sheets-Sheet3 mm ag win es;

@ 17, 1935- J. H. SLAKEYR ET AL WHEELED SCRAPER Filed Sept. 12, 1932 9Sheets-Sheet 5 Dec. 17, 1935.

J. H. SLAKER ET AL 2,024,483

WHEELED SCRAPER Filed Sept. 12, 1932 9 Sheets-Sheet 6 Dec. 17,1935. 4.H;SLAKER ETAL 2,024,483

I I WHEELED SCRAPER Filed Sept. 12, 1932 9 Sheets-Sheet 7 1 z; 257 I 1 IAZM, gkw wzzmamm Dec. 17, 1935.

J. H. SLAKER El AL 2,024,483

WHEELED SCRAPER Filed p 12, 1952 9 Sheets-Sheet 8 Dec- 17, 1935- J. H.SLAKER El Al. 2,

' WHEELED SCRAPER Filed Sept. 12, 1932 9 Sheets-Sheet 9 wlnass PatentedDec. 17, 1935 UNITED STATES 2,024,483 WHEELED SCRAPER Joseph H. Slakerand De Mar A. Palmer, Aurora, Ill., assignors, by mesn'e assignments, toWestera-Austin Company, Aurora, 111., a corporation of IllinoisApplication September 12, 1932, Serial No. 632,706

37 Claims. (o1. 37-129) The present invention relates generally toscrapers such as are employed for grading, lev-.-

eling and digging operations, and has particular reference to scrapersof the type which are 5 mounted on wheels or crawler treads and areadapted to be propelled by a tractor or other pulling vehicle. C One ofthe general objects of the invention is to provide a scraper of thistype characterized by improved mechanism for moving the scraping pan orscoop between the various positions which it assumes relatively to theimplement frame. The pan has three principal positions; a loading ordigging position where the cutting edge of the i5 pan is engaging thesoil for loading the soil in the pan; a transport position where the panis raised out of contact with the soil for carrying its contained loadof soil to a point of dumping; and, a dumping position where the pan istipped for dumping its contained load of soil.

With reference to the mechanism for moving the pan between its threepositions, another object of the invention is to provide improved powerlift mechanism utilizing kinetic energy for rais- 25 ing the pan fromdigging position to transport position and for tilting the pan fromtransport I position to dumping position. This improved power actuatedlifting mechanism dispenses with the necessity of springsand equivalentarrange- 30 -ments which have heretofore. been widely employed forlifting the loadedpan from digging position to' transport position' Inprior constructions in which suihcient potential energy is stored in thesprings to raise the fully loaded 35 pan from digging position totransport position,

' numerous diificulties and objections are encoun tered, such as .thediillculty in some cases of holding the digging Pan 'down in properdigging engagement with the soil, the necessity in 40 some cases ofmaintaining the power transmission clutches in a continuously slippingengagement during the entire digging operation for. resisting thetendency of the springs to elevate the pan, the likelihood of thesprings weakening becoming incapableoi raising a heavily loaded pan,etc. All of these difficulties and objections are avoided in the presentconstruction, which uses no springs for effecting any of the move-.

ments of the pan. I 50 This power operated lifting mechanism pref erablyderives its power-from the traction energy of the supporting wheelsor-crawler treads (although the invention is not limited to aconstruction deriving its power only from traction energy), and anotherobject of the invention is to provide improved mechanism fortransmitting this traction energy to the pan. In this regard, it is oneof the objects of the invention to pro vide improved clutch mechanismfor controllably transmitting this traction power to the lift- 6 ingmechanisms This clutch, mechanism is preferably of the friction type andembodies improved means for maintaining the frictional engagement 'ofthe clutch through its predetermined range of movement notwithstandingthe 10 fact that the clutch engaging control member moves directly withthe driven clutch element. This improved constructionavoids thetendency, present in some prior constructions, for the frictionalengagement of the clutch to diminish with 15 the rotative movement ofthe driven clutch element, requiring continued and further actuation ofthe clutch actuating devices to maintain the clutch in powertransmitting engagement.

A further object of the invention is to provide improved locking means,preferably of the tog gle type, for releasably holding the pan raised inits transport position. This improved looking ,mechanism functions whomthe loaded pan in transport position, after'an initial operation of thepower lift mechanism for raising the pan to this position fromits digginP sition, and preparatory toa later operation of the power liftmechanism for raising the pan todumping position; and also functions tohold the empty pan intransport :position, after the first lower-' ing ofsaid pan from dumping position to, trans- 1 port position andpreparatory to the second lowering of said pan from transport positiondown to digging position."

A further object of the invention is to provide an improved arrangementofcontrol apparatus and connections whereby the actuation of a singlecontrol member is operative selectively tocause engagement of saidclutches 'or to cause 49 the release of said locking mechanism. Inthussimplifying the control operations necessary to be performed,theimplement is made more adaptable to use in tandem'or'train operation,and

the control of one or more implements by a sin-'- gleoperator. or by thedriver of theltractor is I facilitated.

A further object 0'1 the invention is to provide improved means forcontrolling the position of the pan when digging and whenbeing trans- 50ported, and for controlling the movement 0! the panbetween dig ng D$iti0n and transporting efiiciently holding the pan in proper diggingposition against the action of the large stresses bearing against thecutting edge of the pan, and for holding the pan in transport positionagainst the action of the load of soil in the pan tending to tilt thelatter.

The construction embodies a draft connection between the pan and aforward portion of the implement frame for sustaining the draft stressesacting against the cutting edge of the pan, and it is a further objectof the invention to provide improved means for releasing this draftconnection when the pan is to be upended for dumping. In this regard, itis one of the objects to provide an improved construction andarrangement which will effect this release of the draft connectionautomatically in the movement of the Dan.

Another object is to provide improved means for cushioning or yieldinglyretarding the drop of the pan from dumping position to transportposition, so as to avoid objectionable shock and racking of themechanism. In this regard, another object of the invention is to providean improved checking mechanism which will automatically hold the pan inits dumping position, without attention on the part of the operator, fora suflicient interval to insure complete dumping of the load, even whenthe load consists of sticky material.

Another object of the invention is to provide an improved scraper ofthis general type having an improved relation of end gate forapproximately closing the pan during transport, which end gate ismovable automatically to different positions in the loading and dumpingpositions of the pan.

Other objects and advantages of the construcscription of a preferredembodiment thereof. In the accompanying drawings illustrating suchembodiment:

Figure 1 is a perspective view of the scraper, withthe pan raised totransport position;

Figure 2 is a plan view of the construction, a portion of the framebeing broken away;

Figure 3 is a fragmentary side view showing the pan lowered to diggingposition, the rear portion of the view corresponding to a longitudinalsection taken just inside the adjacent wheel and its clutch mechanism;

Figures 3A, 3B and 3C are schematic diagrams for better illustrating theforces and movements involved in the lifting of the pan from diggingposition to transport position;

Figure 4 is a longitudinal sectional view on a slightly smaller scalethan Figure 3, illustrating the pan raised to its transport position;

Figure 5 is a view on approximately the same scale as Figure 3,illustrating the pan upended to dumping position;

Figure 6 is a transverse sectional view taken approximately 011 theplane of the line 6-6 of Figure 2, illustrating some of the controlconnections fo engaging the clutches and for releasing the togg e locks;I

Figure 7 is a fragmentary perspective view illustrating the relation ofthe lost motion collars which actuate the toggle lock tripping lever,and illustrating one method of fastening the chains which'govem thecutting depth of the pan when in the digg ng operation; I

Figure 8 is'a detail view illustrating one end of the axle and showingthe mouii ting of the treads, such as are commonly used on tractorsFigure 9 is a transverse sectional view through 0 the embodiment ofclutch mechanism illustrated in Figure 8;

Figure 10 is a view similar to Figure 8, illustrating a modifiedconstruction of clutch;

Figure 11 is a transverse sectional view through 1 this modifiedconstruction of clutch;

Figure 12 is a view similar to Figures 9 and 11,

. illustrating another modified construction;

Figure 13 is -a fragmentary detail view illustrating an arrangementproviding for the automatic release of the draft connection between thepan and the implement frame, preparatory to the lifting of the pan todumping position;

Figure 14 is a fragmentary side view of a modified arrangement of thecontrol or actuating parts, adapted to transmit equalized operatingenergy to the two power clutches;

Figure 15 is a frontelevational view thereof, a part being shown insection;

Figure 16 is a horizontal sectional view taken 3 approximately on theplane of the line |6|6 of Figure 15;

Figure 1'7 is a fragmentary plan view illustrating another embodiment ofour invention using an end gate for the front end of the pan;

Figure 18 is a fragmentary vertical sectional View, illustrating thenormal position of this end gate when the'pan is in transport position;

Figure 19 is a similar view illustrating the position which the end gatemay assume when the 3 pan is tilted up to dumping position;

Figure 20 is a similar view, illustrating more of the pan, and showinghow the pile of earth entering the pan during loading can raise the Iend gate to a non-obstructing'position;

Figure 21 is a fragmentary side view, illustrating the use of a modifiedconstruction of checking cylinder; and

Figure 22 is a detail sectional view through this Referring first toFigures 1 and 2, the main supporting frame, indicated generally at F, issupported by ground engaging elements typically represented by the twoside wheels 20, 20. While it is preferable for most conditions ofoperation 5 to have the frame supported on wheels, it may be desirablefor operating in extremely soft soil, or

under other adverse conditions, to have these ground engaging elementsin the form of creeper closely spaced parallel front portions Ila, whichare then bent outwardly to f0rm-diverging side portions 2 lb and whichare then bent rearwardly cylinder, on a larger scale. 45

to form widely spaced parallel rear portions He, 65

between which the load carrying pan is mounted. It will be understoodthat separate bar sections can be joined together to form these portionsof the frame, if desired. Suitable cross plates, generally indicated at22 and connect the for- 70 structure are two converging plats ll, whichform a draft attachment having a vertical series of holes 26 enabling adraft clevis 21 to be suitably positioned at any desired height for themost effective transmission of draft to the scraper. Referring to Figure2, the rear ends of the frame bars are cross-connected by aheavy tube 28which may be riveted or welded to the ends of the bars 2|, these pointsof attachment also being reenforced by diagonal gusset plates 29 whichare riveted or welded to the tube and to the frame'bars. A split sleeve34 is riveted or welded to the intermediate portion of the transversetube 28 and has rearwardly extending ears 34a for receiving a draft pin35 (Figure 4) by which a hitch connection can be established to anothertrailing scraper. The front part of the widened rear portion of theframe is alsoocrossbraced by another tube or channel, 35, (Figures 2 and6) which has its ends riveted or welded to the side channels 2|, 2|adjacent to the points where these channels are bent to form theforwardly converging portions 2lb-. An operator's platform 31 is builtabove this converging portion of the frame structure, consisting of aseries 5 of-longitudinal slats 38 secured to cross bars 39 which havetheir ends suitably attached to the frame channels; A guard rail 4| issuitably anchored to the frame structure to extend around the forwardportion of the operator's platform.

The wheels or other ground engaging elements 20 have rotatable mountingon a transverse axle 44, preferably on roller bearings, as illustratedin Figure 8. As shown in the latter figure, the axle 4 4 has rotatablemounting at each sideof e the frame in bearing brackets which are boltedto the top flanges and to the webs of the two side channels 2|.Referring to Figure 1, the intervening span of the axle is preferablyarched or bowed upwardly as indicatedat 44a in order to 140 avoid theaxle obstructing the movement of soil back into the pan. As will behereinafter descrlbed,,;improved clutch devices are associated with eachwheel or ground engaging element 20 whereby the rotative movement ofsaid elements 45 can be transmitted to the axle 44 for causing the axleto lift the pan from digging position to transport position, and fromtransport position .to dumping position. While it is preferable toemploy a rotating axle through which power is transmitted from theclutches to the lifting f mechanism, in order to compel bothv liftingmechanisms to operate simultaneously and to the same degree,nevertheless the construction -may, be such as to transmit power fromthe clutches to the, lifting mechanism independently of the axle.

The pan is generally indicated at" and is.

as a separate plate having flange portions riveted to the bottom andside walls of the pan, and ha v ing its upper "edge reenforced by atransverse angle iron 52-. Bolted to the bottom of the pan, "at spacedintervals across its width, are inclined runners. as shown iii-Figure 3.when the is in its loading or digging position these runners slide onthe soil along'the bottom of the cut and assist in holding the pan atthe proper cutting angle. Said runners can be adjusted relatively to thepan for changing the cuttingangle 5 of the pan, as by inserting flllerplates between the pan and the rear leg of each runner.

Figures 3, 4 and 5 illustrate the three principal positions: into whichthe pan is mo able:digging, transporting and dumping. There are 10 threeprincipal mechanisms or elements which efiect the movement of the panbetween these positions and which properly hold and guide the pan, viz:(1) The power lift mechanism comprising a rotatable powerlift arm 56 anda lifting 15 link 51 connecting this arm with the pan; (2) the draftconnection in the form of a'link 58 which establishes a releasable draftconnection between the pan and a forward portion of the frame; and (3)the controlling or guiding link 59 which as- 20 sists in holding the panin the proper digging position when down and whichalsoaids in holdingthe pan approximately level when in transport position. It will beunderstood-that each of these three mechanisms or devices 55-51, 58 and25 59-is duplicated on each side of the pan.. The

side walls of the pan are provided with substantially V-shaped notches6| extending down from the upper edges of these side walls, -whichnotches embrace or accommodate the axle 44 30 when the pan is intransportand dumping positions. Each lifting link 51 is preferablyslightly bent or curved intermediate its ends and the inner side of thiscurve constitutes an arcuate bearing'surface 51a (Figure 3). When thepan is 35 movingdrom transport position to dumping position this bearingsurface 51a bears against the cylindrical bearing surface 62 of a collar53,

which collar is mounted on the axle 44 just inside of. the adjacent axlebearing bracket 45 (Figure 46 8). When the pan is in transport position,this arcuate bearing surface 51a is preferably slightly spaced from saidbearing surface 52. The arcupan is in either of these positions, the panper- 50- ating entirely satisfactorily in constructions in which thisspaced relation is maintained.

Referring in more detail to' the lifting mechanism 56'-51, the lower endof the lifting link 51 is pivotally connected to a'pivot stud 61 whichis 55 anchored in a reenf'orcing plate 68 secured to the lower forwardportion pf the pan. The upper end of said link 51 is pivotally mountedon a pivot bolt or stud 59 which is-supported in the lifting arm 55.This lifting armis of sector shape, as

best shown in Figure 5, being preferably constructed in the form of aradial "web or flange projecting outwardly from the collar 63 (Figure8'). The collar 53 is secured fast to the axle 44 and whenever powerdriven rotatiomE-is trans- 65 mitted to the axle the collar 63 andlifting arm 56 rotate directly therewith. Aspreviously remarked, thewheelsor other .grgu'nd engagingelements 20 are operative to transmitrotative movement to the axle 44 thrpugh the engage- 7o ment' ofclutches which are generally indicated at 12 and which will behereinafter described. The pivot stud 59 connecting the "lifting link 51with the lifting sector 55 is disposed adjacent to the rearward end ofsaid sectonand the link extends down to its connection with the panaround the rear side of the axle 44. The forward portion of said sectoris provided with an upwardly and rearwardly curved hook 15 forming acurved socket 16. A toggle mechanism 11, 18 is adapted to cooperate withthe hook 15 in holding the pan in its transport position. This togglemechanism comprises a long rearward link 11 and a short forward link 18,the two links being pivotally connected together at a knuckle pivot 10.The forward link 18 is secured to a rotatable pivot shaft 8| which ismounted between an outer bracket plate 82 and an inner bracket plate 83,both of which are suitably secured to the frame structure. At the rearend of the rearward link 11 is a pin 86 which is adapted to engage inthe socket 18 under the hook 15. Preferably the rear link 11 isconstructed of two spaced bars so that it is in effect a double link,and, likewise, the forward link 18 is also composed of two spaced bars.Hence, the two bars of the rearward link 11 form a yoke structure whichstraddles the arcuate rim of the sector-shaped lifting arm 58, with thetransverse pin 86 in position to engage in the socket 16 under the hook15. This arcuate peripheral portion of the lifting sector is widenedslightly, adjacent to and around the socket 16 for giving a greater areaof bearing engagement for the pin 86 when in said socket. The toggle 11,18 is adapted to be folded to a forward and downward position asillustrated in Figure 4, in which position a straight line drawn betweenthe pins 19 and 86 passes below or through the axis of the pivotfshaft8|, whereby this past center relation holds the toggle locked againstrearward pull exerted by the lifting sector 56 against pin 86. Thetoggle assumes this condition when said lifting sector 56 has been swungforwardly to the position illustrated in Figure 4, at which time thelifting link 51 has raised the pan 48 to transport position. The lockedcondition of the toggle with the cross pin engaging in the hook socket116 prevents backward oscillation of the lifter 56, thereby holding thepan in transport position. To drop the pan to digging position it isonly 1 necessary to break the toggle by eifecting such upward movementof the forward link 18 as will carry the toggle pivot 19 up beyond itspast ceng/ ter relation, whereupon the lifter 56 can rotate rearwardlyfor permitting the pan to lower. In the dumping operation illustrated inFigure 5, a the lifting sector continues its forward rotation beyond theposition illustrated in Figure 4, and in such further forward movementthe forked end'of the toggle, together with its cross pin 86, merelyrides on the arcuate upper surface of the moving lifter. The influenceof a spring is constantly exerted on the toggle, tend'ng to swing thetoggle links into the locked position illustrated in Figure 4, so thatwhenever the lifting member 56 is given power actuation for raising thepan from digging position to transport posiv tion the resultant forwardrotation of the'hook projection 15 will permit the toggle mechanism 65to swing forwardly automatically under this spring action. whereby thetoggle w'll automatically lock, This spring action is obtained byrigidly fa'stening the two spaced bars of the forward link 18 to. thepivot shaft 8| and by extending this pivot shaft inwardly or outwardlyfrom the inner or outer, bracket plates 83, 82 to carry a torsion spring81 thereomas shown in Figures 2 and 6. One-end of this spring isanchored to the pivot shaftli and the other end is anchored 75 to theadjacent bracket plate 82 or 83, whereby the torsion of the spring tendsconstantly to rotate the pivot shaft 8| and link bars 18 in a forwarddirection.

The cutting depth to which the pan can be lowered can be varied throughadjustments es- 5 tablished through chains or like flexible members 0i,there being one of these chains at each side of the pan. The rear end ofeach chain is linked to an arm 92 which projects radially from the hubof collar portion 62 of the lifting segment 56, the arm havingreenforced connection with said collar as best shown in Figure 8. Thelinks at the forward end of said chain pass down through a. keyhole slot94 which is formed in a horizontal plate 38a extending rearwardly fromthe side portion of the operators platform. The effective length of eachchain 9| can be varied by engaging different ones of the. links in thenarrow portion of the keyhole slot, and in this manner the extent towhich the arm 92 and lifter 20 56 can swing backwardly in the loweringmovement of the pan can be adjusted.

All of the above described parts having to do I with the pan moving andlocking operations performed through the link 51 are disposed in thespace between the inner side of the frame channel 2| and the side wallof the pan, and all of these parts are duplicated at the other side ofthe pan.

Referring now to the control mechanism which 30 effects the release ofthe two toggle mechanisms 11, "at opposite sides of the pan, and whichalso controls the engagement of the two clutches 12 associated with therespective wheels 20, this control mechanism preferably comprises asingle 35 operating lever ml which is mounted to swing about the axis ofa transverse control shaft I02. As shown in Figure 6, the end portionsof said shaft are rotatably supported in bearing brackets I03 which aresecured to the frame channels 2| or to the plates 38a, and the ends ofsaid shaft projecting outwardly beyond these bearings have crank armsI04 secured thereto. These crank arms have linked connection with theparts which cause engagement of the two power clutches 12, which will belater described. Rotatably mounted on the shaft I02 are two sleeves I05,I05 which have upwardly extending parallel arms I06, I06 at their innerends. The upper portions of these spaced arms converge together andbecome the control lever IOI. ounted in the space between these lowerarm portions I06 is a sector-shaped arm or plate I01 having a lower hubportion which is rigidly pinned to the shaft I02. An inertia responsivelatch I08 cooperates between the lever IM and the plate I01, wherebywhen the lever IN is drawn forward relatively slowly the latch compelsthe plate I01 to move therewith, but when the lever is jerked forwardquickly the inertia latch is released for permitting the lever to moveforwardly independently of the plate I01. The latch I08 normally rideson an arcuate periphery of the plate I01, in position to engage againsta shoulder I00 on said plate when the lever is drawn forwardly. Saidlatch-is pivotally mounted between the lower spaced arm portions I08,I08 of the lever on a transverse pivot pin III, and projecting beyondand up the back side of the lever is an extension of said latch having aweighted end I00a. A light spring I I2 is coiled about the end of thepivot pin land has one end hooked to the lever and the other end hookedto the weighted extension I00a, whereby the latter extension is'normallypressed forwardly against the back side of the lever with the latch noseI08 down in position to engage the shoulder I09. A U-shaped strap H4 issecured to the weighted extension and extends forwardly around the frontside of the lever to limit the range of separating movement between thelever and the weighted extension when the lever is jerked forwardquickly. A transverse stop H5 (best shown in Figures 14 and 15) issecured to the rear portion of the plate or arm I01 and extends acrossthe back sides of the lower spaced 1 ways tend to return the sleeves I05and the lever IOI back to their normal retracted position, and

the lever in returning to such position engages the cross bar stop II5on the sector plate I01 and returns the latter, together with the shaftI02, back to their normal positions. Fastened on the end portions ofsaid sleeves I05, I05 are collars I22, which are preferably secured tothe sleeves by set screws I23 or by any other suitable means enablingthe angular positions of the collars to be adjusted relatively to thesleeves. Disposed adjacent to said latter collars are cooperatingcollars I2 4 within which the sleeves are freely rotatable. Theserotatable collars carry' rearwardly extending bent levers I 25, each ofwhich has a T-shaped outer end adapted in its upward swinging movementto engage the under sides of the toggle link bars 18 for swinging said.toggle links to released position.

Referring to Figure 7, each collar I22 has a lug or shoulder I21, andeach companion collar I24 has a cooperating lug or shoulder I28projecting into the path of movement of the shoulder I21. The normalspacing between the lugs I21 and I28 is such that they do' not engagefor transmitting motion from the collars I22 to the collars I24 andtheir toggle releasing levers I25 until after the lever IOI has beenmoved forwardly a distance corresponding to its range of movement forcausing engagement of the clutches 12, which range of movement n theillustrated construction is approximately 35. That is to say, f theactuation of said lever is to cause engagement of the clutches it isdrawn forward comparatively slowly so as to cause movement of the sectorplate I01, shaft I 02 and levers I 04 directly therewith, and duringthis range. of clutch engaging motion, illustrated as being ofapproximately 35, there is no motion transmitted from the collars I22 toi'he collars I24, owing to the lost motion relation between the lugsI21, I28; whereas, if the actuation of said lever is to effect thereleasing of the toggles, it is drawn forward quickly so as to throw theinertia latch I08 to, inoperative position, whereby the, sector plateI01 does not move therewith, andin this operation after the lever IGIhas moved through approximately 35 of its motion the lugs I 21, I28engage and thereafter-the-T-shziped levers I25 are swung upwardly forreleasing the toggles.

Referringnow to the clutches I04 carries a pivot'I3I (Figure 3) .towhich 9. rearwardly extending link 132 is connected. Said these twolinks at pin I43 is 12 and. their actuating connections, the lower endof each arm which a threaded front portion of the link screws,

whereby the effective length of the link can be easily adjusted. Therear end of each link I32 is pivotally connected at I35 to a lever I36which is pivoted at its lower end on a pivot bolt I31 5 carried by theframe channel. These parts are disposed between the frame channel andthe adjacent wheel. The upper end of the lever I36 carries a pin I38 towhich the forward ends of two links I39 and I39a are pivoted. The linkI39 has an angularly projecting stop shoulder I39b at its end which isadapted to engage the back side of the companion link I39a so as tolimit the .relative spreading movement between said links,

for a purpose which will be presently described. Therear ends of saidlinks are 'pivotally' connected by pins I4I to two shifting links I 42,both of segmental shape, which form an expansible and contractiblesemi-ring, adapted in its expanded form to establish an arcuate guidetrack 2 for exerting pressure against the clutch operating lever whichexpands the clutch band. Thetwo segmental links embrace the axle 44 andthe rear ends of said links are pivotally connected by a pivot pin I43.The pivotal connection between preferably such as arcuate contourbetween the two links at their point of juncture when the links areexpanded, the joint shown in Figure 8 comprising a tongue extending fromone link into a bifurcated end of the other link. The connecting pin I43projects outwardly from the side of to leave a. smooth .the two linksand is pivotally mounted in the upper end of a swinging lever I44, whichhas pivotal mounting at its lower end on a. pin I 45 car- 35 ried by theadjacent frame channel. A stop lug I46 projects outwardly from the topof the frame channel into the path of movement of the lever I 44 forlimiting the rearward swinging movement lines in Figure 9), at whichtime the ring segments I42 are collapsed and the clutch operat- 0 inglever 'I48'is in the inner dotted line position. In this normal ortransport position, theroller I49 on the end of the said clutchoperating lever I48 occupies the dotted line position designated A inFigure 9. When the pan has been swung up to dumping position saidroller, with its'arm' I48, has moved toward or into the dotted lineposition designated B; and when the pan has been lowered to diggingposition said roller, with its arm I48, has moved toward or into thedotted line position designated C. Starting with the pan in its normaltransport position, rearward thrusting movement transmitted through linkI 32 and lever I 36 to the ring segments I42 causes the connectedportions of the segments to press outwardly against the roller l49,swinging it and its lever I48 outwardly to clutch engaging position,indicated by the outer dotted line position of said lever. C ontinuedmotion transmitted to the ring segments 7 causes them to expandoutwardly to the positions indicated in the outer dotted circles inFigure 9. In this position they define a semi-ring substantiallyconcentric with relation to the axle 44, being prevented from spreadingfurther by the enside of the link I39a. With the engagement of theclutch and the concurrent expansion of the ring segments to thisposition, the clutch engaging lever I48 and roller I49 swing up towardor into dotted line position B, corresponding to dumping position of thepan. Notwithstanding the fact that the lever us swings bodily with B.Likewise when the roller is in digging position C, the coaction of leverI44 with stop I46 compels the segments to expand outwardly against saidroller when the clutch is to be engaged.

The driving element of the clutch comprises a drum I54 having an outerperipheral flange I55 enclosing the clutch parts. This driving elementis suitably secured to the hub bf the adjacent wheel or other groundengaging element 28. The driven element of the clutch comprises a discI56 which closes the open face of the drum I54 and which has a centralhub portion I51 suitably keyed to the axle 44. A plurality of shelfbrackets I58 project inwardly from the disc I56 at angularly spacedpoints for supporting a clutch band I59. A suitable facing I62 on theouter surface of said band is adapted to be forced into grippingengagement with the inner surface of the flange I55 when the band I59 isexpanded.

The clutch actuating lever I48 is secured to a shaft I69 journaled inthe disc I56 and extending into the clutch housing. At its inner endthis shaft has a cam I64 secured thereto which is adapted to act againsta pressure block I65 secured to one end of the clutch band I59. Theother end of the clutch band has a lug I66 secured thereto, to which alink I61 is pivoted at I68. The other end of said link is pivoted to aslide block I1I which has adjustable mounting in a slotted guideway I12formed in the disc I56. An adjusting screw I14 disposed on the outsideof the clutch assembly has threaded mounting in a guide boss and has itsinner end connected with the slide block I1 I whereby manipulation ofsaid adjusting screw is operated to shift said slide block inwardly oroutwardly and thereby to expand or contract the clutch band foradjustment purposes. A plurality of tension springs I16 are connectedbetween the shelf brackets I58 and suitable lugs projecting from theclutch band, so as normally to retract said band out of clutchingengagement with the external flange I55.

- The movement of the pan in dumping direction, Figure 5, is limited bythe forward edge of each lifting segment 56 striking a stop shoulder I18which projects inwardly a short distance from the inner side of eachframe channel. The dumping will ordinarily be instantaneous andconsequently the operator will usually release the clutches as soon asthe lifting sectors strike the stops I18, but if it is desired to holdthe pan momentarily in its extreme dumping position, as for dumping clayor other sticky material, such can be effected by properly slipping theclutches 2,024,488 gagement of the shoulder l99b against the backslightly, or the pan can be vibrated back and forth in its dumpingposition by alternately engaging and releasing the clutches. Even if theclutches are held in firm gripping engagement after the lifters 56strike the stops I18, there is 5 no damage as this only results inslipping the wheels 29 over the ground.

Referring now to the draft bar mechanism 58, these draft bars areduplicated at opposite sides of the pan, with each bar pivoted to theforward 10 lower portion of the pan on a pivot stud I84 projectingoutwardly from the reenforcing plate 68. As shown in Figure 2, the twobars converge forwardly and have their front ends extending forwardly inparallelism. These parallel front por- 15 tions are cross connected by apin I86 which is adapted to swing upwardly into the box-like spacebetween the parallel front portions 2Ia of the frame channels. Theintervening length of said pin between the two draft bars 58 is 20adapted to engage with a draft hook I88 which has pivotal mounting on acrossshaft I89 supported in the frame channel portions 2Ia. The pin I86and hook' I88 constitute cooperating latching parts of a releasable.draft latch which 25 transmits draft from the forward portion of theframe to the pan. In the embodiment described, when the pan is in itsdigging position and when it is in its transport position the pin I86remains in cooperative association with the draft hook 30 I88, butpreliminary to elevating the pan to its dumping position (Figure 5) saidpin is released from the draft hook, whereby the draft bars 58 can swingbackwardly for accommodating the tilting movement of the pan. In theembodi- 35 ment illustrated in Figures 1 to 5 inclusive, the pin I86 anddraft hook I88 are released from each other by the performance of amanual releasing operation, and in the embodiment illustrated in Figure13 the releasing operation is 4; effected automatically by the movementof the pan. Referring first to the embodiment of Figures 1 to 5inclusive, the path of swinging motion of the pin I86 is defined by twoparallel supporting links I9I which, at their forward swing- 4:, ingends, have lateral bosses I9I in which the pin I86 is mounted. The upperends of these spaced links are mounted on a transverse pivot rod I92which has its ends supported in brackets I98 secured to the framechannels, suitable spac- 55 ing sleeves being mounted on the rod I92 tomaintain appropriate spacing between the links I9I and between saidlinks and the brackets I98, as clearly shown in Figure 2. A foot pedalI95 is pivotally mounted at I96 on a short standard I91 55 rising fromthe cross plate 28. The portion of the pedal adapted to be depressed bythe operator's foot extends rearwardly and downwardly under thetransverse pivot rod I92, and is adapted to be held elevated against theunder 60 side of this rod by a tension spring I98 extending between thepivot standard I91 and a lug proiecting from the pedal lever. The otherend of said lever carries a pivot bolt I99 which engages in a slot 2IIIin the upper portion of a tripping 65 link 282, the lower portion ofwhich link is pivoted at 288 to the draft-hook I88. The draft hook isnormally held in a depressed position latching over the pin I96 bygravity and by a tension spring 204 which extends between a lu 10 on thedraft hook and a forward point of fixed attachment on the frame. Anextension fail 285 may be provided on the draft hook for engaging theunder side of the plate 22 to limit the downward motion of the drafthook. When the draft bars 58 are to be released in order to permit thepan to be tilted up to its dumping position, the pedal I95 is depressed,as shown in Figure 5, thereby operating through the link 282 to raisethe draft hook and separate the latching shoulder I88a of said hook fromthe pin I86. The pin I89 is prevented from moving upwardly with the hookin this releasing operation by the provision of two arcuate stops 286projecting inwardly from the front portions 2Ia of the frame in positionto be engaged by the bosses I9I' on the links I!" for limiting upwardand forward movement of the pin I86. The slot. I in the link 282 permitsthe hook I88 to move upwardly 223 enga for holdi g the link on the stud.The stud is in the relatching operation without causing movement of thelever or pedal I95. When the hook I88 is to be tripped through a remotecontrol rope or cable. this rope ,is fastened directly to the hook andthe pedal I and link 282 are preferably removed.

When the empty pan swings down from its dumping position back to itstransport position it is desirable to cushion or retard such. returnmovement so that the stopping of the pan in transport position will notcause shock or racking of the mechanism. Accordingly, we have provided ahydraulic dash-pot 208 which is operatively connected between the linksI9I and a point of attachment on the frame. The rear end of the dash-potcylinder is pivotallyconnected at 289 (Figure 5) between a pair of lugs2| I (Figure 6) projecting forwardly from the transverse bracing tube36. A piston rod 2I2 extends from the head end of the cylinder and ispivotally connected to abolt 2 I4 extending between the parallel linksI9I The piston rod 2 I2 is attached to a piston within 'the cylinder,which piston has either a forwardly facing-cup washer of rubber orleather, or any suitable check valve embodied within the piston andarranged whereby the piston can move rearwardly .in the cylinderunimpeded, but when the piston is compelled to move forwardly by thelowering movement of the pan from dumping position the oil in thecylinder is trapped in front of the piston and has a restricted egressthrough or around the piston for checking the downward movement of thepan.

Referring now to the two guiding or controlling links 59 at oppositesides of the pan. it will be seen from Figures 3 and 8 that the forwardend of each link is provided with a bear ng hub portion 2! which isrotatably mounted on the collar 93 encircling the axle 44, this hubportion being confined laterally between the axle hearing 45 and thelifting arm 56. Said hub 2I8 is preferably divided into two halves whichare bolted together over the collar 63, in order to facilitateassembling the guide links over the axle collar. The rear portion ofeach link 59 is bent downward slightly 'and at the end is provided witha slot, 22I extending substantially lengthwise of the link. Engaging inthis slot is a stud 222 which has an outer head or washer ng over theouter side of the link 59 secured to a bracket 224. which is riveted orotherwise rigidly secured to the side wall of the pan. Preferably. theinner end of the link 59 has pivotal mount ng on the frame on an axisconcentric ,wlth the axis of the lifter 56, such being established bythe pivotal mounting of said'link around theaxle. collar 93, but thearrangement is not essentially limited to such concentric mounting. Theslot 22I establishes a lost motion relation in the controllingconnection 59 extending between this inner pivotal axis 44 on'the frameand the outer pivotal axis 222 on the pan, but such lost motion relationmight be established between the inner end of the link and the 5 axis 44or it might be made-to occur within the body of the link. As hereinafterdescribed, when the pan is in digging position the control link 59 isoperative to function as a compression member and when the pan is intransport position this link is operative to function as a tensionmember. a

Figures 3A, 3B and 3C diagrammatically illustrate the cooperation of theparts 51, 58, 59 and in governing-the movement of the pan from d gingposition to transport position and in governing the relation of the panin these positions. When the pan is lowered to digging position, as

"illustrated in Figures 3 and 3A, the engagement of the runners 54against the bottom of the cut 20 retains the forward edge of the paninclined the rear end of the pan is prevented from tilting 5 upwardly bythe two guide links 59. with reference to this function of said guidelinks, it will be evident that in the forward motion of the implement alarge force is acting against the forward cutting edge of the pan, asindicated by 30 the directional arrow F. Since the draft force isapplied to the pivot I84 at a point above the point of application ofthe reversely acting force F, it will be evident that a rotative coupleis created in the pan tending to swing its rear end 35 upwardly aroundthe draft pivot I84 as a center. The direction of this rotative force isdiagram- 'matically indicated in Figure 3A by the arc A passing throughthe pivot stud 222. At this time each pivot stud 222 is at the inner endof the 40 slot 22I of its guide link 59. Therefore, since the link 59and stud 222 can at this time only swing upwardly about the arc B,concentric with the axle 44, the rotative tendency represented by thearc A merely forces the stud 222 against 45 the inner end of the slot HIand establishes a compression stress in the ink 59, whereby the 'linkholds the rear end of the pan against tipping upwardly unde'rthe actionof the force F. Referring now to Figures 33 and 30, when the 5 liftingmechanism is actuated the lifting links 51 apply a force acting upwardlyand rearwardly on the lifting pivots 61. This lifting force is appliedto the pan intermediate the link pivots I84 and 222 but closer to thefront end of the pan, 55 and such lifting force has a rearward componentalong the line between the pivots 61 and 69. The first action of thislifting force is to swing the front end of the pan upwardly around therear ends of the runners 54, which remain in'sliding so contact with theground during this initial lift, owing to the fact that thepreponderance of the weight of the pan and the load therein is behindthe point of application of the lifting force at the pivots 61.. Thisinitial upward tilting of the 55 front end of thepan serves theadvantageous purpose of settling the load back into the rear portion ofthe pan. During this initial lift ng movement a draft load iscontinuously maintained on the draft links 58 by reason of the drag ofthe runners 54 on the ground and by reason of the slight rearwardcomponent in thelifting force exerted on the pivots 61. The upwardlifting of the front end of the pan ceases as a tilting motion as soonas the studs222 engage the 75 rear ends of the slots 22 I, andthereafter the upward movement of the pan is one of direct lift.

The relative movement between the studs 222 and slots 22I, which causesthe studs to engage thev rear ends of the slots, comes about by reasonof the weight of the load in the pan tending to swing the pancounterclockwise with respect to the pivot centers 61 and 69, and alsoby reason of the slight movement which the draft pivots I84 can have ina rearward direction in moving upwardly along the are C. The parts areso proportioned that the studs 222 engage the rear ends I of the slots22I when the draft pivots I84 are still a considerable distance below astraight line extending between the points I86 and 222, as indicated bythe dash and dot lines in Figure 3B. While the pan was in diggingposition with the force F acting against its cutting edge, the draftlinks 58 were in tension and the guide links 59 were in compression. Assoon, however, as the studs 222 engage the rear ends of the slots 22I,in the above described direct lifting movement of the pan, this relationof forces is reversed, i. e., a compression force is established in thedraft links 58 and a tension force is established in the guide links 59.

It will therefore be seen that approximately as soon as the studs 222move backwardly and engage the rear ends of the slots 22I in the upwardtilting of the front end of the pan, the lifting movement thereaftertransmitted to the pan compels the latter to move upwardly with a bodilyshifting or translatory motion of the pan. When the pan reaches itsfinal position for transport the draft links 58 and guide links 50 arein approximately the positions illustrated in Figures 30 and 4. Theclutches are released as soon as the toggle locks 'II--'|8 snap intolocked position, and thereupon the pan is held in its transport positionby the toggles. Any continued engagement of the clutches after the panreaches trans? port position cannot accidentally dump the pan but merelyexerts increased pull on the draft links 58, owing to pressureengagement between the curved portions 51a of the lifting links 51 andthe curved surfaces 62 of the axle collars 63 tending to rotate the pan,but since the draft links '58 are still latched to the frame thiscontinued engagement of the clutches only results in slipping of thewheels 20.

When it is desired to dump the pan the pedal I95 is first actuated tolift the draft hook I88 out of engagement with the pin I86, andthereafter the clutches are again engaged by pulling the control leverIOI forwardly with a relatively slow, steady movement for producingcorresponding motion of the sector plate I'I. The releasing of the draftbars 58 permits them to swing backwardly as the pan swings upwardly tothe position illustrated in Figure 5. As previously remarked, the panmay be held in this upended dumping position by properly slippingtheclutches, and is quickly returned to transport position when theclutches are released. This return movement of the pan from dumpingposition to transport position is cushioned by the retarding action ofthe ,cushion cylinder or dash' pot 208, as previously described. Duringthe time that the pan is moving up toward and down away from dumpingposition the pins 86 at the rear ends of the toggle locks are ridingidly over the outer track portion of each lifting arm 56, and when thepan is fully returned to transport position these pins engage in thehooks 15 of the lifting arms for holding the pan in transport position.At the same time,

the draft links 68, in swinging forwardly, restore the pin I86 intolatched engagement with the draft hook I88. When it is now desired todrop the pan to digging position, the control lever IOI is given a quickforward jerk, whereby it is freed from the sector I01, and thereaftercontinued forward movement of said lever operates through the arms I25to release the toggle locks IL-I8 for permitting the pan to drop down todigging position. 10

It will be seen that in the embodiment hereinbefore described allcontrol operations are performed simply by the manipulation of thecontrol lever IN and the draft tripping pedal I85. Both of these areconveniently accessible to an operator standing on the operator'splatform 31. If it is desired to have the tractor driver actuate thesecontrols from his seat on the tractor, such can be easily provided forby the arrangement of control connections illustrated in full lines inFigure 4. In this arrangement, a suitable standard 23I is erected at thefront end of the frame, having a bracing atp by the operator from hisseat on the tractor serves to perform the same control operationspreviously described. When two or more scraping implements are connectedtogether in tandem behind a tractor they may all be controlled by thetractor driver, or by an operator standing on the platform of the frontscraper. As illustrative of this arrangement, we have shown in dottedlines in Figure 4 a supporting standard 23I' which is substantially aduplicate of the standard 23I and which may be mounted on the frontimplement at the rear of the operator's platform for supporting pulllines extending back to the control devices of the rear implement. Therear implement would preferably have a standard 23I mounted at itsforward end, as illustrated in full lines in Figure 4, for, guiding thecontrol cables to the tripping pedal and to the control lever. Whenoperating a plurality of implements in tandem the control connectionsmay be arranged for simultaneous raising and dropping of all of thepans, or they may be arranged for selective raising and dropping of thepans of the different implements.

Figures 10 and 11 illustrate a modified construction of clutch mechanism12. In this embodiment, the clutch actuating arm I 48a is mounted on ashaft I03a which is rotatably supported in the driven clutch elementI56, in the same manner as described of the embodiment of Figures 8 and9, but the inner end of this shaft I63a carries, in lieu of the cam I64,an arm I64a carrying a'roller I64b. When the arm I48a is swung outwardlyto its clutch engaging position the roller I64b is pressed outwardlyagainst the inner side of an arcuate plate I650. which is secured to theinner side of the clutch band I59 at a point adjacent to one endthereof. The resulting outward pressure of the clutch band against theflange I55 of the driving clutch element causes this end of the band torotate with said flange (in the direction of the arrow) and therebycauses the entire band to expand outwardly against said flange,whereupon the driven clutch element rotates with the driving clutchelement. The length of the arcuate plate I65a is suflicient to remain incontact with the roller I64b in the slight angularmovement of the bandrelatively to the driven clutch element as the band is expandedoutwardly against the flange I55. If desired, an adjusting screw I14(such as shown in Figure 9) 'may be provided to coact with the link IBMfor adjusting the clutching action of the band. In the ordinary use ofthe implement the pan will be raised to transport position (Figure 4) orto dumping position (Figure 5) while the implement is travelingforwardly in a substantially straight line path, and at this time thetwo clutch mechanisms at opposite sides of the pan will transmit thesame rate of rotative movement from their respective wheels to the axle44. However, the operations of lifting the pan to transport position orof lifting the pan to dumping position,

can also be effected while the implementis travcling through a sharpcurve, or even if the implement is being swiveled on one wheel, withthis inner wheel remaining stationary or even rotating backwardly. Thisis because the above described clutch mechanism of Figures 10 and 11 isonly operative to exert effective clutching engagement between thedriving and driven clutch elements when the wheel and drum I54 of thatclutch mechanism are'rotating forwardly, owing plate I6,5a mounted onthe inner side of the band I59, in substantially the same manner asdescribed of Figures 10 and 11. In this embodiment, however, the arcuateplate IBM is secured to an intermediate portion of the band I58, andboth ends of the band are pivotally connected-to links IIiIb which havetheir inner ends mounted .on pivots IIlb. Springs IIGb are-connected tothe links I6'Ib onto the ends of the band for normally holding thelatter in non-clutching rela-' tion. It will be evident thatirrespective of the direction of rotation of the driving clutch element,when the roller 'arm I84a causes outward pressure on the plate segment"$511 a snubbing action will occur between that point of the band andthe end of the band extending in the direction of rotative movement. Ifdesired, an adjusting screw or screws I14 (Figure 9) may be arranged tocooperate with one or both of the link pivots II lb for adjusting thegripping action ofthe band.

In each ofthe preceding embodiments, the expansion of the ring segmentsI42, I42 may be the clutch actuating lever in its position of maximumclutch engagement. Qn the other hand, the ring segments I42, I42 mayonly be expanded part way, or their-expansion may be contracted portionI86. links I9Ia are pivotally connected at I920, to a supporting bracketstructure I93a, in much the after an initial complete expansion, forobtaining a partial or slipping engagement of the clutch at any point inthe rotative movement of the driven clutch element.

In Figure 13 we have illustrated a modified 5 embodiment of latchingconnection between the front end of the draft link and the frame, whichlatching connection is automatically released when the pan is liftedfrom digging position to transport position, thereby avoiding the neces-10 by the transverse pin or spacing sleeve I86 at the front ends of saiddraft links, and the supporting links I9Ia are pivotally connected with20 the draft links on a transverse pivot pin I 9Ib which is spacedrearwardly from the latch ng The upper ends of said supporting samemanner 'as described of the preceding embodiment. The piston rod '2I2 ofthe cushioning cylinder 288 is also operatively connected at 2I4 tothese supporting links I9 la. The latching hook I88 is also pivotallymounted on a heavy transverse pin I89 extending between the closelyspaced front portions of the frame channels. A stop lug 285a at theforward end of said hook is adapted to engage anadjustable stopconsisting of a-set screw 238 which threads down through a tapped bosson the plate 22 and which, has a lock nut 239 for securing said setscrew in any adjusted position. If desired,a suitable spring, like thespring 284 of Figure 3, may be operatively connected with the latchhook, normally tending to swing said hook downwardly. The nose portionof the latching hook hasa protruding V-shaped edge I881) which, when itis below the medial thrust line passing through the latching collar I86,tends to cam-this collar upwardly into the recessed portion of the hookupon rearward pull being exerted on the draft links, and which; when itis above this medial thrust line, tends to cam this collar I86downwardly out of engagement with the hook. When the pan is down in itsdigging position the draft links 58 assume approximately the angularityillustrated in the dotted line position in Figure 13. This places thelatch portion I86 of the draft links within the embrace of the latchinghook. As the pan is raised from digging position up to transportposition the rear ends of the draft links swing upwardly therewith, andwhen the pan has arrived in transport position, or is just approachingthis position, the draft links assume the more nearly 60 horizontalposition approximately illustrated in full lines in Figure 13. Thiscausesthe latching portion I86 to be swung downwardly to the point wherethe medial thrust line through this latcha ing portion is disposed belowthe edge I88b of .the latching hook. Thereupon, when the pan is swungup'to dumping position the draft bars 58 are free to swing backwardlywith thepan. By appropriately adjusting the set screw 238, the point atwhich the two latch members I86 and I88 are free to releaseautomatically can be adjusted to occur just at the time the pan reachestransport position, or at any earlier point in the upward movement ofthe pan'from digging position to transport position. Arcuate stops28811,

ment, in dispensing with the manual control necessary in the case of thetripping pedal I96, greatly simplifies the operation of the implement.It will be understood that, if desired,'the point of latch release maybe made to occur between the draft links 58 and the pan, in .either amanually operated embodiment or an automatically operated embodiment.

Referring to Figures 2, 3, and 4, it is desirable to provide curvedguides 24I, mounted fixedly on the inner sides of the frame channels 2|for cooperation with the lifting pivots 61 in those constructionswherein a checking or cushioning cylinder, such as the cylinder 208, isarranged to exert its checking force on the pan through the draftconnections. These curved guides are shown as consisting of curvedsections of angle bar having their. longitudinal flanges riveted to theweb portions of the frame channels and having their curved transverseflanges projecting inwardly to a sufficient depth where they can beengaged by the lifting pivots 61. The lifting pivot studs 61 haverollers or projecting portions 61a (Fig. 17) which extend outwardly asufficient distance so as to be able to engage the guides. The

draft pivots I84 and draft links 58 lie considerably closer to the sidesof the pan, so that they are not in the fore and aft plane of saidguides. The rollers or end portions 61a of the pivot studs 61 bearagainst these curved guides 24I as the pan swings down from dumpingposition to transport position. Thus, notwithstanding the checkingaction which the cushioning cylinder 208 is opposing to'forward movementof the draft links 58, these curved-guides compel said return movementof the pan to occur rotatively substantially around the axle center andto'occur substantially concurrently with the return motion of the axlesothat the pan and links will resume the proper transport positionsillustrated in Figure 4. If desired, the guides 24I maybe provided withthe upwardly and forwardly inclined deflecting surfaces 242 at theirforward ends, to aid in restoring the parts to their proper positions inthe event that the draft connection should become accidentally releasedwhile the pan is moving forwardly in digging position.

In Figures 14, and 16 we have illustrated a modified arrangement of theclutch actuating connections whereby there is always assured thetransmission of equalized operating effort 'to both clutches. The twotoggle tripping sleeves I05, I05 have their inner ends secured to theupwardly extending spaced arms I06, which arms have their upper endsjoining into the control lever I0I, in substantially the-same relationillustrated in Figure 6, except that the lower arm portions I06 arespaced further apart to accommodate the equalizing connections. brackets245 are secured to the frame or opera- .tors platform soas to providebearing support for the inner ends of said sleeves. In this, modifledembodiment, instead of having a single shaft I02 extending from sidetoside of the machine for operating both clutch actuating arms I 04, thereSuitable bearing links 25I which have yoke-shaped extremities ,25Ia attheir forward ends. The rear ends of said bolts or links are threadedfor the reception of nuts 252 bearing against the back sides of the arms249, by the manipulation of which nuts the 15 effectivedengths of thelinks 25I can be adjusted for individually adjusting the engagement ofthe clutches. The yoke shaped extremities of said links embrace the endsof an equalizing bar 254, being pivotally connected to the ends of saidbar by pivots 255. The center of said equalizing bar 254 is pivotallyconnected by a pin 256 between two vertically spaced ears 251 projectingforwardly from the sector plate I01. The mounting and the operation ofthe inertia responsive latch I08 are substantially the same aspreviously described. I

When the lever IllI is jerked forward quickly, preparatory to releasing,the locking toggles, the

operation is the same as described of the preceding embodiment, theinertia responsive latch I08- rising to clear the shoulder I09 onthesector plate I01, and continued motion-of the lever IOI serving torotate the sleeves I05 independently of the shafts I 02. When the leveris drawn forward relatively slowly, however, for causing engagement ofthe clutches, the latch I08 engages the shoulder I09 and results in thesector plate I01 moving correspondingly. with the lever. The rockingmounting of the equalizing bar 254 on the 40 plate or arm I01 causes anequalized pressure to be transmitted through the links 25I and arms 249to the two shafts I02, whereby any tendency of one clutch to engageahead of or to the exclusion of the other is prevented. The plate or armI01 has the previously described cross bar H5 at its rear edge forengaging the rear sides of the arms I06, so that this plate or arm isrestored to normal position when the control lever IN is returned tonormal position. As previously described, it is the action of thetension springs H9 exerting pressure. through the arms H6 and sleeves405 that restores the lever I III to normal position when forwardpulling effort on the lever is released. 5.? In Figures 17, 18, 19 and20 we have illustrated how an improved arrangement of end gate may beemployed on our wheeled scraper for better retaining the load in the panduring transport. The

gate, designated 264 in its entirety, comprises a transverse plate 265having its upper and lower margins bent laterally to form the stiffeningflanges 265a and 265b. Spaced inwardly from the ends or sides of saidplate are two vertical angle bars 266, each of which has one of itsflanges se- C5 cured to-said plate 265., Forwardly extending supportingarms 261 arefastened to the. other flange of each angle bar, and thefront ends of said arms 261 are apertured to receive pivot pins or bolts268. These pivot members extend between pairs 01' depending pivot plugs269 extending downwardly from the underside of the transverse bracingtube 36. It will be noted from FigureslB and,19 that the lower edge ofeach gate supporting arm 261 is inclined upwardly and forwhereby thegateis raised to a non-obstructing position.

Figure 18 shows the gate in its normal closed position for substantiallyclosing the open front end of the pan when the pan is in transportposition. The gate is retained in this position by two short arms orbrackets 212, which are rigidly secured'at the outer upper corners ofthe plate 265 and which extend forwardly for resting on the, comers ofthe horizontal plates 38a extending rearwardly from the side portionsofthe operators platform. In the preferred construction the gate isspaced slightly fromthe' side walls and from the bottom wall of the panwhen the pan is in transport position, there being no necessity ofactual contact between the gate and the pan to hold the load in the pan,although such contact or approximate contact can-be provided for in-theconstruction if desired. All of the remaining parts of the machine,includingthe pan and its several link connections, are the same aspreviously described. When the pan is swung downwardly to diggingposition its sidewalls pass slightly beyond and overlap the side edgesof the gate. As shown in Figure 20, with the pan moving forwardly indigging position, a slope or rise of earth E accumulates in front of thepan and this sloping rise of earth reacts upwardly againstthe inclinedrunner plates 2" on the botand its load are swung upwardly to transportposition, the pan moves rearwardly, as previously described, so thatwhen the pan. arrives in its transpor position, illustrated in Figure18, the gate 26 substantially closes the front end of the pan. If anyrocks, or other portions of the load project forwardly from thepan inpositionto strike the lower edge of the gate, the gate is free to risetherewith until this projecting portion of.

1 tured dogs at the other end of the cylinder has .jpivotal attachmentto the supporting links I 91 a.

the load is shaken ofl'xor is moved back into the pan whereupon the gateresumes its normal closing position. If desired-the runner plates 21l'may be utilized to raise the gate when the pan is tilted upwardly todumping position, as we shall now describe.

- Referring to Figure 1'1, when the pan is in its transport and diggingpositions, and is moving between these positions/the parallel rearportions 580 of the draft links 68 are substantially in the .transverseplane of'the gate, but since these rear portions are spaced outwardlybeyond the sides of the gate they transmit no movement thereto.

When the pan is tilted upwardly to its dumping position (Figure 19), therearward'movement of draft links 58 brings the diagonal portions 581? ofthese two links into contact with the slop- 7 ing plates 2" secured tothe under sides of the gate supporting arms 261,as indicated in dotted[lines in Figure 17 and in full lines in Figure 19; Hence, during thisdumping movement of the ing of the contents of the pan. Whenthe pan isswung backto its transport position after dumping, the gate dropsback'to its normal potion.

sition with the stop arms 212 resting on' thestationary side plates aaa.

In Figures 21 and 22 we have disclosed an im=-, proved construction ofmechanism for checking or controlling the movement of the pan fromdumping position back to transport position. ,In its preferredembodiment this controlling mechanism is in the form of a hydrauliccylinder, 288, somewhat similar to the previously desbribed hydrauliecushioning cylinder208. The action is similar to that of the cylinder208 in that the cylinder 208' has the additional feature ofholding thepan upended inits dumping position for a considerable time interval,before allowing the 1 pan to swing down through the remaining part ofits travel. The advantage of such operation is that the operatoronlyneeds to engage the clutches for a sufficient time to bring the pan upto-dumping position, whereupon the clutches 2 can be released, afterwhich the pan is automaticaly controlled so as to remain in thiselevated dumping position for a considerable time interval before itstarts back totransport posi- The two main relatively movable partsofthis construction comprise thecylinder 288' and 'a piston 28l therein.The piston is secured to a piston rod 282 which extends out through aguide boss 283 formed on an end head'284 which closes 3 one end of thecylinder. Two-packing washers 283a are pressed inwardly ,bycoi1,springs283b against the rod 282. The head-285, closing the. otherend of the cylinder has any suitable attachment or mountingmeansthereon, such as a pair of spaced lugs 286 projecting therefrom forreceiving a pivot bolt- 281.

The cylinder is operatively connected between themovable sup rting linksl9la and the trans verse bracing tu 86. In the arrangement illustrated,the piston rod 282 is extended rearwardly through vertical slots 288provided in the front and rear walls of said tube, and the rear end ofsaid piston rod is pivotally connected at 289 to lugs 29] projectingfrom the rear side of the tube. The pivot bolt 281 extending between theaper- By connecting the piston rod 282 to the back side of the bracingtube 26, a longer length of cylin- 5;

der can be employedwithln the'available space, and a stronger attachmentfor the piston rod is obtained, although, if desired, this arrangementmight be reversed by connecting the cylinder 208' to the bracing tube 36and by connecting the pis- .3 ton rod 282 to the links lgla. Also, whilewe have shown this improved formof checking cylinder 288"a's beingconnected with "the automatically releasing type of draft connectiondisclosed in Figure 13, it will be understood that such checks C ingcylinder may be used with equal advantage. in association with themanually released type of draft connection illustrated in Figures 3, 4and 5.

Referring now to the checking mechanism within the cylinder, a. cupwasher 292, of leather, C5

nut 294 screwing over a reduced threaded end 70 of said rod. 1 f V Thecylinder is substantially fllled with oil and when the cylinder travelsto the left thisoil can pass rather freely around the piston 28I andpast the cup washer192 into the lefthand end of the 15

